Hydraulic machine tool



Aug. 15, 1944.

E. P. BULLARD, 3D

HYDRAULIC MACHINE TOOL Filed Dec. 27, 1940 3 Sheets-Sheet 1 ATroRNEi! ug. 15, 1944. E, P B| 1| 7 3D 2,356,028

HYDRAULIC MACHINE TOOL Filed Dec. 27, 1940 3 Sheets-Sheet 2 n) A :qu Emi um f um u... .1 D .1 65mm lla w .s

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INVENQTOR B Edwaral. BLdlard/E ATTORN Aug. 15, 1944.

E. P. BULLARD,A an

HYDRAULIC MACHINE TOOL` Fild Dec'. 27, v 1940` 3 Sheets-Sheet 5' ff/f//f v/ GEARRAISING AND SYNCHRUNIZING CAM INV NTOR \r EdwardPBullaJ/'i Patented Aug. 15, 1944 UNITED STATES PATENT OFFICE Edward P. Bullard, IH, Fairleld, Conn., assgnor .to The Bullard Company, acorporation of Connecticut Application lDecember 27, 1940, Serial No. 37.1,;859

V21 Claims.

This invention relates to 'machine tools and particularly to fluid-operated mechanism for moving a tool holder toward and away from -a work-supporting member.

Machine tools of the type that employ Aa cam and follower forlcontrolling the movement yof a tool support toward and `from the work-supporting member usually include a 'doublel track cam, namely, one having effective surfaces on either side-of vthe cam follower, and Vprovide relative rotation between the cam Aand the tool support during an operation. Machine tools of ythis type are required to move'the tool support at a relatively rapid speed toward and from thework-supporting member prior to, and aftera workingoperation, during the latter of which the tool support is fed at a relatively slow rate toward the worksupporting member. Due to the limitations i-I'nposed upon such ystructure including the practical cam angle for such work, a greatportion of the relative rotation between the Vcam drum and the tool support -is required -for non-productive operatic-n, such as the traverse movement -of the Itool support toward and away from the worksupporting member. Additionally, in such machine -tools, the stroke of the tool support is dennitely limited by the diameter of Ythe cam drum.. Any substantial stroke of the tool support vrequires a cam -drum of impractically large diameter because a relatively long cam :path is yrequired to move the tool support throughout the substantial stroke. l

An object of this invention is to provide a. machine tool of `the above described type which includes mechanism that will overcome Tthe above as well as other difculties encountered in prior known `machine tools of this type.

Other objects of the invention include Vthe provision of a machine tool in which the tool support is adapted to be moved toward rand -away from the work-supporting member at a relatively rapid speed during a relatively small portion of the rotation `between the toolV support and the tool-support feeding cam; the provision` of a machine tool in which the tool support is restrict'- ed toa predetermined rate of movement toward the Work-supporting member but unrestricted -with -respect to movement away Vfrom said-worklsupporting member; the provision of `arriachine tool in which the tool support Ais moved toward and from the work-supporting ymember by' fluidoperated means having snubbing characteristics;

:the :provision of a machine tool in :whichthe tool support is adapted tto be moved .toward andaway from the work-supporting member Iby fluid-foperated means'in which separate fluid-pressure means is lprovidedxfor vthe traverse and the ,feed strokes of the tool support; .the provision of suc-h a machine -tool in which -the fluid-pressure means for :thetraverse operation of the tool support yis employed 4to veffect adequatelubrication of the machine; ythe provision `of'a machine tool including.4 a work-supporting member and a tool Isupport adapted to be moved relatively toward and from each other by vhuid-operated ,means including I'separate valve-actuating means `for the traverse and feed movements of the tool support, and wherein relatively rotatable mearis is provided for selectively. operating :the valve-actuatingm'eans; the provision Eof a machine tool Vhaving la' work-supporting member that is adapted to be connected to, and disconnected from a continuously rotating positiveV drive and in which synchronizing mechanism is provided f or insuring Athat the work-,supporting vmember is rotatin'gr at the speed .at which the continuously rotating `positive driving means is rotating prior to effecting a connection between the two; .and the provisionkof `a lmultiple spindle machine tool having4 a plurality of tool supports andworkspindles that areadapted to Abe moved about a central column, and in which the tool supports are iluid operated and Acontrolled by valve mehanism rendered eiective by a stationary cani member.

The above, other objects'andnovel ,features of the invention will `become .apparent `from the following description takenwith the accompanying 'drawings in which:

`Figure 1 is a sectional elevational view 0f ,a mltiplespindle machine tool vt0 which the prin- 'ciples'of the invention vhave been applied;

Fig. 2 is a sectional plan :View takensubstan- -tially along .the klineg2-2 Qf Figs. l and 4;

'v Fig. '13 is 4afsectional plan View taken substan- .itially along .line .V3- .13 :of Figs. .1 .and 4:

Fig. :4 isa stretch-.outfsectonal e1evationa1 .view taken .substantially'valonglines 4--4 cf Figs. 2

"Fig l5 is a diagram showing the development ,of :the feed vcam Vand .thennath'f travel of the camzfollofwer `'that is connectedzto the .tool support; e ',Flg. 6 isanenlarged sectional elevational View fof the work supporting 'member synchronizing Fig. 'l isa-camlayout of the actuating means `forfthe:synchronizing mechanismof Eig.16,; and

e i-Fig. ,8'is` .a layoutof ,the valveactuating mechanismofFig.1. v

i Referring to the drawings,-yparticula-rly Fig. l,

the invention is shown as applied to a multiplespindle machine tool of the type disclosed in Patents 1,574,726 and 1,804,971 granted to E. P. Bullard on Feb. 23, 1926, and May 12, 1931, respectively.

The machine tool comprises a base B to which a standard S is rigidly xed. The standard- S provides a support for a rotatable carrier C that is adapted to support a plurality of rotatable work-supporting members such as spindles S. The carrier C is adapted to be continuously rotated at a relatively slow speed about the standard S during a working o-peration, while atl the same time the individual spindles S' are adapted to be rotated about their axes. The stationary standard S is adapted to support a cam drum D near its upper extremity. The upper portion of the cam drum D forms a support for a motor which is adapted to drive transmission gearing extending downwardly through the stationary standard S and operatively connected to the individual spindles S. A housing H, fixed to the carrier C and surrounding the stationary standard S, is adapted to provide slide bearings in alignment with eacli of the work-supporting spindles S for tool holders T that are adapted tobe reciprocated toward and from the worksupporting spindles S. The tool-supporting members T are adapted to be moved toward and away from the spindles S' by fluid-operated mechanisms F and, during a working operation, the cam drum D is adapted to restrict the rate of movement of the tool supports T toward the work-supporting spindles S. The cam drum D, however, does not interfere with the free movement of the tool supports away from the spindles S.

During a portion of rier C, work W that has from the spindles S the rotation of the carbeen finished iS removed and unfinished work is placed thereon. Obviously, during this time the tool support T must be at its elevated position -in order'not to interfere with the removal and replacement of the work W. The carrier C rotates continuously at a relatively slow rate dur- -ing the operation of the machine tool, and

should the cam drum D be employed to move the tool holders T away from the work-supporting spindles, a great portion of the rotation of `the carrier C about drum D would be consumed because the maximum cam angle that can be emrployed would require a cam track that would cover a substantial portion of drum D. Furthermore, if the cam drum D is made large enough in diameter to provide ample time to raise the tool holders by cam means, the proportions of the machine become impractical.

The present invention contemplates employing the fluid-operated means F in combination with the cam drum D having a cam track that is substantially entirely effective for work. The fluid-operated means is adapted substantially instantaneously to raise the tool supports T to their highest positions thereby providing maxi- `mum time within which to remove completed work and to replace it with unfinished work.

During the removal from, and the replacement of the work on the spindles S', they, of course, must be stopped. Furthermore, after a new piece of work is mounted on the spindles S', they must be connected to continuously rotating driving means. v Accordingly, synchronzing mecha- -nism lVf is provided with each spindle for accomplishing this result.

Referring to Fig. 1, the base B comprises a casting I, cored out to provide a chamber for a quantity of lubricant that is employed for operating the fluid-operated means F and also for lub-ricating the working parts of the machine tool. The casting I0 is provided with a centrally disposed annular rib II to which the standard S .is rigidly connected through a collar I2 by bolts I3. The standard S comprises a relatively long hollow member I4 having a solid base portion that is machined for housing various driving gears for a purpose to be described later. The upper extremity of the hollow standard I4 rigidly supports a cylindrical bracket I6, to which a transmission housing I1 is rigidly united. A motor mounting I8 is fixed to the top of the housing I1 and supports a motor I9 for driving a transmission within the housing I1 to be described later.

The carrier C comprises a disc-like casting 20 having a central opening 2l that includes a race- Way 22 for an anti-friction bearing 23 between the carrier C and the lower extremity of the vertically-disposed standard I4. The carrier C is provided with a series of openings 24 arranged in a circle about the casting 20 and adapted to receive the work-supporting spindles S. A worm gear 25 is connected to the carrier C and meshes with a worm 26 that is driven by a motor 21. Therefore, the carrier C is rotated constantly during the operation of the machine tool at a relatively slow rate of speed by a motor separate from the motor I9 which latter drives the spindles S' as will be described.

The spindles S are of usual construction and each is provided with spaced bearing portions in the carrier C. They are adapted to be driven by the motor I9 through a transmission mechanism as follows: The motor I9 is adapted to be coupled to a vertically disposed shaft 25' to which a spur gear 26 is keyed. The gear 26 meshes with a gear 21' on a stub shaft 28. The lower end of the shaft 28 xedly supports a gear 29 that meshes with a similar gear 30 on a relatively long shaft 3|. The shaft BI extends ydownwardly through the center of the standard I4 and at its bottom fixedly supports a spur gear 32. The gear 32 meshes with a similar spur gear 33 on a stub shaft within the base of the standard I4. An internal-external gear member 34 is journaled about the base of the standard I4,the internal teeth thereof meshing with the teeth of gear 33, while the external teeth thereof are adapted to mesh with a plurality of spur gears -35 of the respective synchronizing mechanisms M for each spindle S'. A spur gear 36, associated with each of the mechanisms M, is adapted to be driven from the gear 35 through Y,the synchronizing mechanism. These gears 36 are adapted to mesh with their respective spindle gears 31 which latter are keyed to the spindles S'. From the foregoing it is apparent that motor I9 is capable of rotating all of the spindles S and that by changing the gears 3S and 31, ,different rotative speeds of each individual spindle S may be obtained.

The housing H comprises a substantially hollow casting that is adapted to be rigidly xed to the carrier C by bolts 38. The upper portion of the vhousing H is provided with a plain bearing surface 39 that mates with a corresponding bearing surface on the upper portionof the stationary standard I4. A hollow cylindrical bracket 40 is xed to the upper extremity of the housing H, and is adapted to rotate therewithas the car-- rior. C is v,rotated during operation. The upper portion rof the bracket is provided with a retaining bearing 4| that vprovides a sliding connection between it'A andthe fixed housing |1. Two series of openings fI2-and42l are-provided about the outer surface of the bracket 40 thereby exposing the drum D.A

Although there is a tool support T and actuating mechanism F of substantially the same construction for each work-supporting spindle S', only one such tool support T and its Vmechanism F is disclosed and will be described.

Referring to Fig. 1, the central portion ofthe rotatable housing H is provided with slide bearing surfaces 43 on which the tool supports Tare adapted to be reciprocated. These bearing ,sur-

faces 43, as well as the openings 42, are in alignment with the respective spindles S.4 Accordingly, location of the tool-supporting members T on the bearings V43 places them in cooperative relation with the respective spindles S. Each tool support T includes a slide member 44 in which a tool holder 4'5 is `dovetailed for reciprocation at right angles to the vertical movement of the member 44. The holder 45 is adapted to support one or more tools such as 46 that are moved into engagement with the work W. The support 44 is connectedV to a draw bar 41 that extends upwardly to a location adjacent one of the openings 42. The upper extremity of the draw bar 41 is provided with a follower 48 that is adapted to cooperate with the cam track 49 on the cam drum D. The tool-supporting member 44 is providedwith a connecting rod 50 having a piston 5| at its upper end that is adapted to be reciprocated within a `cylinder 52. The cylinder 52 together with the remainder of the fluidoperated means Fis fixed to the bracket 40 and is adapted to rotate with the housing as is each lof the individual tool-supporting vmembers 44 and its actuating mechanismA F.` Referring again to Fig. l, the base B is adapted to contain a supply of lubricating oil for lubricating the various working parts of the machine tool, as Well as for supplying fluid pressure to the mechanism F. A fluid-operated pump 53 is adapted to be supplied with lubricant from the supply kwithin base B and to deliverthe lubricant under a medium pressure through a conduit 54 that extends upwardly .through the center of the stationary standard I 4.V Theupper end of 'conduit 54 extends -through the wall of the standard I4 and empties into an annular groove 55 formed on the periphery of said standard. A passage 56 within the housing H is formed so that it communicates with the annular groove 55 whereby vupon rotation of the housing H about the stationary standard I4, the passage 56 is continuously supplied with lubricant under a medium pressure. The opposite end of conduit 56, from that which'communicates with the annular groove 55, opens onv the peripheral surface of the housing H. A separate fluid-operated. pump 51, adjacent to pump 53, is adapted to be supplied with lubricant from .base Band it is adaptedV to supply .lubricant under a relatively high pressure through a conduit 58 that extends upwardly through the center of the standard|4 and which opens into an annular groove 59 formedon the outer periphery of the standard. The housing H is providedwith a conduit 60, the one end of which communicates with the annular groove 59 and the opposite endjof whichopens on the periphery of the housing H. f

Referring; toFigures 1A to 4 inclusive, the fluidoperated means for applying lubricant to alter# nate sides of the piston 5| comprises a body portion 6| that is adapted to be bolted tothe bracket 48 such that the passage 56 Will register with a passage` 62 (Fig. 2) and passage 60 will register with a passage 63 (Fig. 3). The formation of 'the various passages for iiuid Within the body portion 6I is effected by drilling. Accordingly, theplaces Where-the drills enter the body portion 6| must be plugged. These openings are all indicated ascontaining plugs 64.

The valve member or body 6| is provided with 'two parallel cylindrical bores 64, l65v within which valve" members 66, and 61 are adapted to be reciprocated; Both the valves 66 and 61 arenor" mally` urged toward their upper positions by springs 68 and 69 upon which the respective valves are adapted to seat. Referring to Fig. 4, the passage 62, which is the inlet of the medium pressure fluid in the valve body 6| communicates with a passage 18 that joins a vertically disposed passage 1I. The passage 1I is located between the passages 64 and 65. Passage 1|'is adapted to communicate with each of these valve bores 64 and 65by passages 12 and 13, respectively.

The passage 63 which serves as the inlet of the high pressure fiuid to the valve body 6| communicates with a passage 14 that joins a passage 15 leading to, and communicating with the bore 64 within which valve stem 66 is located. The bores 64 and 65 are adapted to communicate with each other by a passage 16. The bore 65, within which the valve stem 61 is adapted to reciprocate, communicates with the top of the cylinder 52l through a passage 11, and communicates with the bottom of said cylinder through a passage 18 thence through a passage 19,. Not only `are the passages 11 and 19 employed to de- `liver fluid under pressure to opposite sides of the piston 5|, but they are also employed to carry away or exhaust the fluid from oppositefsides of the said piston. Accordingly, an exhaust passage is adapted to communicate with the bore 65 through an opening 8|. The exhaust 80 communicates with a passage 82 (Fig. 2) that terminates in an opening `83 in communication with a duct 83', formed in the housing H, andl which empties into an annular groove 84 (Fig. 1,) o n the outer periphery of the standard |4. Although the ducts 56, 60 and 83 are in different radial planes, the upper portions thereof are, for clarity, shown in a single plane in Fig. 1.

Referring to Fig. 4, snubbing means is provided for cushioning the action of the piston 5I Aat each -end of its stroke. This means comprises locating the exhaust from opposite sides of the piston 5| at points spaced a predetermined distance from vthe end of the stroke of the piston 5|. For example, therexhaust from the lower side of the `piston 5| passes through an opening 85 that communicates with passage 19. Exhaust from the upper side of' piston 5| passes through opening 86 communicating with passage 11. Springloaded check Valves 81 and 88 are located between passages19, 11 and the entrances to; the cylinder 52l By-passes 89 and 99- are provided around the check valves 81 and 88 so that the fluid that is trapped, after the exhaust passages 85 and 86 are covered by the piston 5|, will be exhausted at a much slower rate, thereby effecting a cushioning action to the piston 5|. Referring to Fig. 4, with the valve stems 66 and 61 in their lower positions as shown, uid under medium pressure enters the passage 62, fiows through passage 10, thence through passages 1|,

13,'.across valve bore 65 into duct 18, thence through vpassage 19, through the check valve 81 andinto the cylinder 52 .below thepiston 5| vcausing the pistoni to;move-upwardly.:v As the piston 5| moves upwardly, the fluid above the piston exits through the duct 86passage 11, into bore 65, throughA duct 8|, into passage 89 and thence tov the exhaust port 89 (Fig.;2). Movement of the valve stern 61,to its upper position permits the fluid under medium pressure in passagef? to travel through passage 1I., duct 12 into.val,ve bore 64,--thence through duct 16, across bore d65, i,nto passage11, vpast the check valve 88 and into the cylinder 52 above thipiston 5I causing the piston I to move downwardly. As the piston 5I moves downwardly, the uid below the piston is adaptf ed .to exhaust through the duct 85, passage 19, duct 18, bore 65, duct 8|, passage 8l) and outwardly through the exhaust port.83 (Fig. 2).

With the valve 61 in its upper position movement of the valve stemA 66,` to its upper position Vpermits the high-pressure fluid enteringport .63 (Fig. 4) to pass through passage 14, conduit 15, across bore 64through duct 16, across bore 65,

into passage 11, through duct 86 and into the .l

cylinder'52 above v.the piston 5I. o

As previously stated, each tool support T is provided with a fluid-operated mechanism F just described, and each such mechanism is adapted to be rotated aboutA the stationary standard I4 with the carrier C. The valves 6B and 61 are adapted to be selectively lowered and released in 'accordance with a predetermined order. That isto say, means is provided in the form of a stationary cam track 9| (Figsfl and 8) fixed to the upper portion of the transmission housing, ,I1 in a position where the successive uid operated means F vwill be actuated to effect a predeterf mined movement of the respective ,tool supports 44. Y t lv f Referring to Fig. 8, wherein is `disclosed the relation of the cams on cam track 9|, reading from vright to left, the rst operation that occurs is the lowering of valve 61 causing the piston 5I and tool support to move upwardly. Later on,l the feed valvev 66 is moved downwardly. These two :operations occur as the spindles S approach the loading position of the machine where the completed work is replaced on the spindles S' by uniin'ished work. After a spindle S has been reloaded,` the traverse Vvalver'l is permitted to .rise asthe valve steml61 passes beyondfthe extent of the cam track 9|, by virtue of the spring 59 forcing it upwardly. i At this point, the-piston 5I is caused to move downwardly rat a traverse rate to lower the roll 48 onto the cam track 49 of the cam drum D, At a predetermined time interval thereafter, the feed vvalve 66 moves beyond the inuence of the cam track 9| and spring 68 causes it to be moved to its upper position whereupon high feeding pressure is admitted to thetop of the piston 5| to maintain the roll 48 in contact 'Withthe cam track-49 of the drum D during. a machining operation on the work W. 'Referring to Fig. 5, the action of the roll 4 during the previously described cycle, as shown in Fig. 8, is disclosed in relation to the development of the feed cam track 49` on the cam drum YD. From the point 92, Fig. 5, to pointl 93 (from right to left), represents the eiective portion of the cam'track 49 on drum D. From the point 93 to the point 92 (from right to left) a safety feature is provided which comprises Ya lportion of cam track that will elevate the roll `A48 and the tool support T above theA work, thereby preventing the worker tool vfrom damaging each other in the yeventthat thehydraulc means fails to function.A During the interval of rotation of the carrier C, when each portion thereof passes the ,track 9 3-92 (right to left Fig. 5) of drum D, the roll 48 and tool support T are elevated to their highest positions and lowered so that the roll 48 rests on the cam 49 within a minimum of time, thereby providing a maximum time interval lwithin which to replace the finished work W with unfinished work.

,During the operation of the machine tool, it `is oftenl'esirable and necessary to move any one .of thetool supports T to its upper position withouty waiting until. the mechanism F is Vacted by the' earn track 9|. Referring to Fig. 4, manually-operable means is associated with each of the mechanisms F for effecting movement of the valve B1 to its lower position thereby causing piston 5| to be raised. An extension of valve stem 61 is provided with la, shoulder 94 with which a pivotal camr95 is adapted to cooperate. Thev cam 95 is connected to a pull rod 96 through 4a lost motion joint 91. The design and arrangement of the parts is such that downward movement of the rod 96 causesk cam 95 to force the stem 61 downwardly and to move said cam to a self-locking position. "Merely forcing rod 96 upwardly releases the stem 61. The rod 96 is adapted to be held in its upper position when not in use by a spring-pressed detent 98.

Referring to Fig. l, the exhaust from the various duid-operated mechanisms F empties into the annularpassage 84 passes through a duct 9,9 into the interior of the standard I4. A connection is provided between the duct 99 and a vertically-disposed lubricating pipe |99. The pipe'l is connected to the conduit 54, and a pressure-relief valve IOI is provided in the pipe for lay-passing the iiuid incline 54 over and above that required for the cylinders 52. The pipe |90 extends to substantially the top of the machine tool and is provided with various ducts suchas |92, |93, etc. which direct the lubricant to the various bearings of the machine tool that require lubrication. Accordingly, the supply of lubricant from the pump 53 that is normally under a medium pressure and employed for traversing the piston 5I in both directions within the cylinder 52, is also employed to provide 'a lubricating system for the machine tool. The arrangement disclosed and Ydescribed maintains a substantially constant lubricating pressure because substantially the amount that is withdrawn from the system for moving the piston 5I in either direction is exhausted into the lubricating system from the opposite side of the piston through the annular passage 84 and duct 99 intothe pipe |90.` Accordingly, no substantial variation in lubricating pressure will occur within the system. v

Referring to Figs. 1, 6 and 7, the carrier C is continuously rotated about the standard I4 at a relatively slow rate by the motor 21, while at the same time, the motor I9 rotates the spindles S through a constantly rotating positive drive. As a spindle S on the carrier C moves past the loading station, and during the time that the -work holder T is in its upper position, it is necessary to stop the spindle, replace the nished` work with unfinished work, synchronize thexspeed of rotation of the spindle and re-connect it to the positive drive. Y

Referring to Fig. 6, the spur gear`35 that remains constantly in mesh with theexternal teeth of gear element 34 is provided with a hub por tion |04 journaled on the lower end of a shaft |05 mounted in an anti-friction bearing |06 Within the carrier C. The gear 35 is provided with a clutch-engaging surface |01 that is adapted to mate with a friction clutch |08 xed to an extended hub portion of the gear 36. An internal ring gear |09 is fixed to the gear 35, and is adapted to mesh with gear teeth formed on the periphery of the extended hub portion of gear 35. The gear 35 is adapted to be axially moved so that the gear portion |09 is disengaged from the teeth ||0 and the clutch engaging surfaces |01 and |08 are engaged.

Relative axial movement of the gear 35 is provided through a resiliently-acting mleans including plungers ||2 mounted within bores ofthe extended hub portion |04 of the gear 35. The plungers ||2 are connected together by a pin ||3 supported in an axially-movable member 4. Springs ||5 and I6 are located within the bores of hub |04 and bear against the plungers ||2. The passages through which the. pin I3 extends are enlarged somewhat at ||1, ||8 so that a slight amount of lost motion may be provided for rendering the shifting means resilient. The member H4 is mounted in anti-friction bearing ||9 so that it can rotate with the gear 35. The means employed for axially moving the member ||4 comprises a shaft |20 that extends into a recessed portion of the member 4 and which is journaled therein in anti-friction bearings. Accordingly, the shaft |20 need not rotate while the member ||4 may rotate. The shaft |20 is rigidly fixed to the forward end of a cam arm 2| that includes a contact portion |22 in alignment with a cam track |23 fixed to the collar |2 on which the standard I4 is rigidly bolted. The developed form of the cam track |23 is disclosed in Fig. 7. It includes an intermediate surface |24 which, when the member |22 rides thereon', causes the' gear 35 to be moved upwardly such that the gear |09 is moved out of mesh with the teeth ||0y but without the `clutch surfaces |01 andv |08 being engaged. Cam |23 also includes a higher surface |25, which when in cooperation with the lever |22 causes the gear 35 to be moved further upwardly such that the clutch surfaces |01 and |08 are frictionally engaged to effect synchronization of the speed of the spindle S with that of gear 35. At the end of the cam |23, a sudden drop off |26 occurs which permits the gear |09 to drop into mesh with the teeth ||0 when both are in synchronism. A spring |21 is provided between the shaft |05 and the member 4 for insuring instantaneous breaking of the clutch engaging surfaces |01 and |08 when the lever |22 falls off the point' |26 of the cam 23.

From the foregoing,

it is apparent that throughout the cycle of operation of the machine tool, the gear 35Y constantly rotates at the' proper speed; that as a spindle vS approaches the loading station, the cam |23 causes the caml arm |2| to raised toits intermediate position thereby disengaging gear 36 from 35 without effecting engagement of the clutch surfaces |01, |08 thereby permitting the spindle S to stop; that near` the end of the loading station, the arm |22 moves to its highest position thereby effecting engagement of the clutch surfaces |01,r |08 and synchronizing the spinne speed with @hater the gears -35 and |09; and finally, when this synchronization has been attained, the engagement of -gear |09 with the teeth |0 is effected.

Although the various features of the improved mechanism have been shown and described in detail to fully disclose one embodiment of the invention, it will be evident that numerous changes may be made in such details, and certain features may be used without others without departing from the principles of the invention.

What is claimed is:

1v. In a machine tool, a work-supporting member; a tool support; a piston -connected to said tool support; a cylinder in which said piston is adapted to lbe reciprocated; means for restricting the movement of said tool support toward said work-supporting member during a feeding operation, said means permitting unrestricted movement of said tool support away from said work-supporting member; means for supplying fluid pressure to opposite sides of said piston for moving said tool support toward and from said work-supporting member independently of said restricting means during a. traverse movement of said tool support; separate iiuid pressure means for supplying fluid to said piston for moving said tool-supporting member in cooperative engagement with said restricting means during a feeding movement; and means for cushioning the action of said piston at opposite ends of its path of travel.

2. In a machine tool, a work-supporting member; a tool support adapted to be moved toward and from the Work-supporting member; means for rotating said work-supporting member; al piston connected to said tool support; a cylinder in which said piston is adapted to be reciprocated; means for supplying fluid under pressure to 0pposite sides of said piston for traversing said tool support toward and from said work-supporting member, said means including means for supplying lubricant at a substantially constant pressure to certain parts of said machine tool that require lubrication; and means for exhausting opposite sides of said piston to said lubricant supplying means.

3. 'In a machine toola carrier adapted to support a plurality of work-supporting members; means for rotating said work-supporting members; a standard; means for rotating said carrier about said standard; -a plurality of tool supports arranged in alignment with said work-supporting members and adapted to be rotated about said standard with said carrier; a centrally lccated stationary cam; means connecting said tool supports to said cam including follower means adapted to rest on said cam; fluid-operated means associated with each of said tool supports, including means for controlling the admission of fluid to said fluid-operated means; and a stationary member adapted selectivelyto operate in succession the fluid-operated means of each of said tool supports as said carrier and said tool supports are rotated about said standard.

4. In a machine tool, a work-supporting member; a tool support; a piston connected to said tool support; a cylinder in which said piston is adapted to be reciprocated; means for restricting the movement of said tool support toward said work-supporting member during a feeding operation, said means permitting unrestricted movement of said tool support away from said work-supporting member; dual pressure supplyV means including means for supplying a relatively low traverse pressure and a relatively high feeding pressure to said cylinder; a valve body associated with said cylinder adapted to contain valves for selectively admitting iiuid under said relatively low pressure to opposite sides of said piston for moving said tool support during a trav-4V ersing operation, and for admitting relatively high pressure iiuid to one side of said piston to marintain said tool support in cooperative engagement with said restricting means during a feeding operation. Y

5. In a machine tool, a Work-supporting member; a tool support adapted tofbe moved toward and away from said work-supporting member; fluid-operated means for moving said tool support including a unitary structure comprising a cylinder within` which a piston is adapted to be reciprocated;.,a valve body and a plurality of valve-actuating means within said valve body; means for supplying separate iiuid pressures to said plurality of valve-actuating means within said valve body; means for automatically actuating said `valve means; means for providing relative movement between said unitary assembly and said valve-actuating means for operating said valve mechanism to selectively admit said separate fluid pressures to said cylinder; and manually-operable means connected to one of said valve means for actuating it independently of saidautomatic means.

6. In a machine tool, a work-supporting member; a tool support adapted to be moved toward and away from said work-supporting member;

means for positively controlling the rate of movement of said tool support toward said work-supporting member, and permitting unrestricted movement of said tool support away from said work-supporting member; unitary fluid-operated means for moving said tool support comprising a piston connected to said tool support; a cylinder within which said piston is adapted to be reciprocated; a valve body associated with saidf cylinder and including a plurality of valve actuating means; fluid-pressure means for supplying fluid to opposite sides of said piston for moving said tool support toward and away from said work-supporting member independently of said controlling means; separate duid-pressure means for supplying iiuid pressure to said cylinder for maintaining cooperation between said tool support and said controlling means during a working operation; means for automatically actuating said valve means in accordance with a predetermined selected order; and manually operable means associated with one of said valve means for moving said tool support away from said work-supporting member independently of said automatic means.

7. In a machine tool, a work-supporting member; a tool support adapted to be moved toward and from the work-supporting member; means:l

for rotating said work-supporting member; a plston connected to said tool support; a cylinder in which said piston is adapted to be recipro-` cated; means for supplying fluid lubricant under pressure to opposite sides of said piston for trav-` ersing said tool support toward and from said work-supporting member; a by-pass leading from said duid-supply means adapted to direct the iiuid lubricant to points of the machineV tool requiring lubrication; a relief valve in said bypass for maintaining a predetermined pressure in the piston supply means; and means for ex-v hausting opposite sides of said piston to ,Said by-pass.

8. In a machine tool, a work-supporting member; a tool support; a cam drum; means for providing continuous relative movement between said tool support and said cam drum while successive pieces of work are operated upon by said machine tool and during the interval between the operation on successive work pieces; a @am track on said cam drum for controlling the movement of said tool support during a working operation; a safety track on said cam drum for moving said tool support away from said work-supporting member during a portion of the relative movement between the cam drum and tool support; and uid-operated means for moving said tool support away from said Work-supporting member substantially instantaneously whereby a maximum of time is provided for removing and replacing work on said work-supporting member during said continuous relative movement.

9. In a machine tool, a stationary standard; a carrier adapted to support a plurality of worksupporting members; means for rotating said work-supporting members; means for rotating said carrier about said standard; a plurality of tool supports arranged in alignment with said Work-supporting members and adapted to be rotated about said standard with said carrier; fluid-operated means associated with each of said tool supports for controlling their movement; means for conveying fluid through said standard; means for conducting said fluid from said stationary standard to said fluid-operated means associated with each of said tool supports; and means adapted to selectively actuate said fluidoperated means for controlling the movement of said tool supports towardand away from said work-supporting members.

10. In a machine too-l, a stationary standard; a carrier adapted to support a plurality of worksupporting members; means for rotating said Work-supporting members; means for rotating said carrier about said standard; a plurality of tool supports arranged in alignment with said work-supporting members and adapted to be rotated about said standard with said carrier; a piston connected to each oi' said tool supports; a cylinder in which each of said pistons is adapted to be reciprocated; a centrally located stationary 50.* cam; means connecting Vsaid tool supports to said cam including follower means adapted to rest on said cam, said cam being adapted to restrict the movement of said tool supports toward said worksupporting members during a feeding operation,

5 5. and permitting unrestricted movement of ysaid tool supports away from said work-supporting members; and means for supplyingfluid pressure to opposite sides of said piston for moving said tool supports toward and from said work-supporting members independently of said restrictmg means and for maintaining cooperation between said follower means and said stationary work-supporting members land adapted to be rotated about said standard with said carrier; a piston connected to each of said tool supports; a cylinder in which each of said pistons is adapted to be reciprocated; a centrally located stationary cam for restricting the movement-of said tool supports toward said Work-supporting vmembers during a feedingoperation, and permitting unrestricted movement of said tool supports away from said work-supporting members; means for supplying fluid pressure to opposite sides of said pistons for moving said tool supports toward and from said work supporting members independently of said restricting means; and separate fluid pressure means for maintaining said tool supports in cooperative engagement with said restricting means.

12. In a machine tool, a stationary standard; a carrier adapted to support a plurality of worksupporting members; means for rotating said work-supporting members; means for rotating said carrier about said standard; a plurality of tool supports arranged in alignment with said- Work-supporting members adapted to be rotated about said standard with said carrier; a piston connected to each of said tool supports; a cylinder in which each of said pistons is adapted to be reciprocated; a centrally located stationary cam for restricting the movement of said tool supports toward said work-supporting members during 'a feeding operation, and permitting unrestricted movement of said tool supports away from said work-supporting members; means for supplying uid pressure to opposite sides of said pistons for moving said tool supports toward and from said work-supporting mem-bers independently of said restricting means; separate fluid pressure means for maintaining said tool supports in cooperative engagement with said restricting means during a working operation; and means for cushioning the action of said pistons at the ends of their paths of travel.

13. In a machine tool, a stationary standard; a carrier adapted to support a plurality of worksupporting members; means for rotating said work-supporting members; means for rotating said carrier about said standard; a plurality of tool supports arranged in alignment with said work-supporting members and adapted to be rotated about said standard with said carrier; a piston connected to each of said tool supports; a cylinder in which each of said pistons is adapted to be reciprocated; means for supplying fluid lubricant under pressure to opposite sides of said pistons for traversing said tool supports toward and from said work-supporting members, said means including means for supplying lubricant at a substantially constant pressure to certain parts of said machine tool that require lubrication; and means for exhausting opposite sides of said pistons into said lubricating supply means.

14. In 1a machine tool, a stationary standard; a carrier adapted to support a plurality of Worksupporting members; means for rotating said Work-supporting members; means for rotating said carrier about said standard; a plurality of tool supports arranged in alignment with said work-supporting members adapted to be rotated about said standard with said carrier; stationary cam means for positively restri-cting the rate of movement of said tool supports toward said work-supporting members; and fluid-operated means associated with each of said tool supports for traversing said tool supports toward and away from said work-supporting members during a minimum portion of the rotation of said tool supports relatively to said cam means, thereby providing la maximum portion of the relative rotation between said calnmeans and tool supports for loading, unloading and working on work.

15. In a machine tool, a stationary standard;

a carrier adapted to support ia plurality of worksupporting vmembers; means for rotating said Work-supporting members; means for rotating said carrier about said standard while successive work pieces are adapted to be operated upon; a plurality of tool supports arranged in alignment' with said work-supporting members and adapted to be rotated about said standard with said carrier; a centrally located stationary cam; follower means associated with said tool supports adapted to rest on said cam; the construction and arrangement of said cam and tool supports being such that completed work is replaced byuncompleted work while said carrier and tool supports move relatively to a portion of said cam; and fluid-operated means associated with each of said tool supports for moving said tool supports away from said work-supporting members substantially instantaneously when said carrier arrives at said portion of said cam.

16. In a machine tool, a stationary standard; a carrier adapted to support a plurality of worksupporting members; means for rotating said work-supporting members; means for rotating said carrier about said standard at a. constant speed while successive pieces of work are operated upon; a plurality of tool supports arranged in alignment with said work-supporting members adapted to be rotated about said standard with said carrier; a stationary cam; a cam track covering a portion of said stationary cam for controlling the movement of said tool supports toward said work-supporting members during successive working operations; uid operated means for moving said tool supports away from said work-supporting members as they successively pass by another portion of said cam; and a safety cam track covering the latter portion of said cam drum adapted to move said tool supports away from the Work-supporting members so that the tools clear the work as the work-supporting members pass said latter portion of said cam drum.

17. In a machine tool, a stationary standard; a carrier adapted to support a plurality of worksupporting members; means for rotating said work-supporting members; means for rotating said carrier about said standard; a plurality of tool supports arranged in alignment with said work-supporting members adapted to be rotated about said standard with said carrier; fluidoperated means for moving said tool supports toward and from said work-supporting members; valve means associated with each of said fluidoperated means for admitting uid pressure to said fluid-operated means; and means for selectively actuating said valve means in accordance with a predetermined order.

18. In a machine tool, a standard; a carrier adapted to support a plurality of work-supporting members; means for rotating said worksupporting members; means for rotating said carrie-r about said standard; a plurality of tool supports arranged in alignment with said worksupporting members adapted to be rotated about said standard with said carrier; a centrally located stationary cam; means connecting said tool supports to said cam including follower means adapted to rest on said cam; :duid-operated means associated with each of said tool supports; valve means associated with each of said fluidoperated means for admitting iluid pressure to said fluid-operated means; and stationary means for selectively actuating said valve means as said carrier and said tool supports moveabout said standard.

19. In a machine tool, a standard; a carrier adapted to support a plurality of work-supporting members; means for rotating said work-supporting members; means for rotating said carrier about said standard; a constantly operating driving means for said work-supporting members; a friction clutch between said work-supporting members and said constantly operating driving means; a releasable positive drive betweenfsaid constantly operating driving means and said Work-supporting members; stationary cam means adapted to selectively dsengage said releasable positive driving means Without engaging said friction driving means thereby permitting the Work-supporting members to stop rotating; means for effecting engagement of said friction clutch means thereby to synchronize the speed of the Work-supporting members with said constantly rotating driving means; and means for simultaneously disengaging said friction clutch means and for engaging said positive driving means.

20. In a machinetool, a stationary standard; a carrier adapted to support a plurality of worksupporting members; means for rotating said Work-supporting members; means for rotating said carrier about said standard; a plurality of tool supports arranged in alignment with said work-supporting members adapted to be rotated about said standard with said carrier; stationary cam means for positively restricting the rate of relative movement between said supports in one direction during a working operation and for permitting unrestricted relative movement between said supports in both directions during traverse; and uid-operated means for providing traverse relative movement between said supportsin both directions during a minimum portion of the rotation of said tool supports relatively to said camy means, thereby providing a maximum portion of the relative rotation between said cam means and tool supports for loading, unloading and operating on Work.

21. In a machine tool, a standard; a carrier adapted to support a plurality of work-supporting members; means for rotating said work-supporting memb-ers; means for moving said carrier about said standard; a plurality of tool supports arranged about said standard; cam means for positively restricting the rate of movement of said tool supports toward said Work-supporting members; means for providing relative movement between said cam means and said tool supports; and fluid-operated means associated with each of said tool supports for traversing said tool supports toward and away from said work-supporting members during a minimum portion of the relative movement between said cam means and said tool supports.

EDWARD P. BULLARD, III. 

